Constant pressure multistage packing



1?, 193$. H. T. WHEELER 291M528 CONSTANT PRESSURE MULTISTAGE PACKING Original Filed May 25, 1951 2 Sheets-Sheet l ATTORNEYS.

May 117, 1938. H. T. WHEELER 2,117,528

CONSTANT PRESSURE MULTISTAGE PACKING Original Filed May 25, 1931 2 Sheets-Sheet 2 7 E 5 ATTORNEYS.

Patented May 17, 1938 UNITED STATES PATENT OFFICE CONSTANT PRESSURE MULTISTAGE PACK- ING Harley T. Wheeler, Dallas, Tex.

3 Claims.

This invention relates to the holding of constant high pressure by a multistage packing in a stuffing-box, and its chief advantage lies in a capability of regulating the seepage flow due to pressure so that saturation of the packing by the pressure will be at the lowest possible value.

Another advantage is that the highest as well as the lowest pressure ranges may be held with a uniform efficiency.

Still another advantage is that packing rings of different density may be used in this invention to regulate the ficw of pressure thru the packing, thereby controlling to a great extent the amount of the friction of contact.

The present application is a division of my copending application Serial Number 539,803, filed May 25, 1931, which has matured into Patent 2,012,150 of August 20, 1935, wherein the construction of the stufiing box is claimed.

Still another and important advantage is that the packing is arranged to regulate the drop of pressure within the packing structure, at the same time regulating the seepage flow due to pressure, so that the friction of contact will be 25 created uniformly over the area of contact.

With these objects in view, other desirable advantages of construction will be disclosed during the description, accompanied by the drawings, wherein:

Figure 1 is a cross-section of the multistage packing built according to this invention.

Figure 2 is an end View of the multistage packing with a partial cross-section along the line 2-2 of Figure 1.

Figure 3 is an upper half view of a compartment along the line 3-3 of Figure 1.

Figure 4 is an upper half view of a compartment along the line 44 of Figure 1.

Figure 5 is a diagrammatic cross-section of a 40 cone-shaped packing ring, with the greatest density at the inner portions.

Figure 6 is a diagrammatic cross-section of a cone-shaped packing ring of uniform density.

Figure '7 is a diagrammatic cross-section of a 45 cone-shaped packing ring with the greatest density near the outer portions.

Figure 8 is an internal pressure chart with the frictioncurves of the packing, using the inside density rings of Figure 5.

Figure 9 is an internal pressure chart with the friction curves of the packing, using the outside density rings of Figure '7.

Referring now especially to Figure 1, the body I is an extension of the machine frame thru 55 which the shaft 2 extends and pressure exists in the clearance between the shaft 2 and the body I. A series of cups, forming compartments between their confines, the face of each being pressure tight one with the other, are held by the bolts 8 concentric with the shaft 2 and pres- 5 sure tight against the body I by means of the gasket 9. Within the confines. of each compartment as formed are placed packing rings, as will now be described in detail.

The spacing ring 3 is adjacent to the gasket 8 and forms the inner seat of the cone-shaped packing rings l0. Each of the cups 4, 5, and 6 has a cone-shaped end-wall against which the packing rings Ill, II, [2 and I3, respectively may rest while under pressure. The spacing ring 3, the cups 4, 5 and 6 and the packing gland i each have a clearance around the shaft to prevent contact. In the end-wall of the cup 3 is shown a series of outlets M for seepage to flow from the packing rings in the compartment between the cup 4 and the spacing ring 3 and into the next adjacent compartment. The seepage which would collect in the packing confined between the end-walls of the cups 4 and 5 is released thru the passages l5, and into the packing rings 12,

and in turn is successively vented thru the passages l6, and finally flows to the atmosphere thru the passages i! made in the face of the gland I. It should be apparent that the cone-shaped endwalls of the spacing ring 3, the cups 4, 5 and 6 30 and the packing gland 1, form compartments of a definite size, in which the packing rings are confined, and that there is no adjustment after the assembly is placed against the body I of the machine.

Referring now to Figure 2, an end view of the cross-sectional assembly of Figure 1: The packing gland l is held to the machine frame by the bolts 8, 8 and the seepage passages IT, H are vents from the outer packing compartment. An end view of the outer cup 6 is shown in partial cross-section and along the line 2-2 of Figure l. The seepage holes [6, i5 vent the pressure from the adjacent inner packing compartment. Around the shaft 2 is shown the fit of the packing rings 12.

In Figure 3 is indicated an upper half end view of the cup 5, along the lines. 3-3 of Figure 1. It may be noted that the seepage passages l5 are of closer spacing than those of Figure 2, and that an inner row of passages l5a has been added, the reason for so doing will be explained later. The packing rings H are shown to be fitting the shaft 2.

In Figure 4 is indicated a lower half end View -packing ring of the cup 4, along the line 4-4 of Figure 1. The seepage passages i i are placed closer to each other than is shown in either of the Figures 2 and 3, and other passages Ma are added. The packing rings 18 are shown to be fitting the shaft 2.

As will afterward be explained, controlling the reaction of the packing to the impressed pressure, necessitates a type of packing ring suitable to the condition. In Figure 5 is a packing ring made so that the density of its structure increases toward the center of the cone-shape and is a maximum at the contacting surface of the shaft, as indicated by the variation in the shading of the edge, and corresponds to those rings made by the process described in my application for Letters Patent, Serial Number 509,622, dated January 19, 1931, now Patent 1,978,240 issued October 23, 1934. Figure 6 is a cone-shaped of uniform density, as indicated by the uniform shading on the edge thereof. In Figure '7 is another type of packing ring in which the density increases toward the periphery, as indicated by the shading of the edge, and reaches a maximum at the contact with the stuffing-box wall, and corresponds to those rings made according to my application for Letters Patent, Serial Number 515,232, dated February 12, 1931, which has resulted in Patent 2,028,961 granted January 28, 1936.

The chief advantage of a porous structure for the packing here used lies in its capability of gradually reducing an impressed pressure to a lower level, thereby distributing the drop of pressure along the area of contact between the packing and the shaft, thus in turn distributing the friction necessary to seal the pressure. It is proven by the first and second laws of friction which have been developed that the thrust of the packing structure against the shaft is equal to the drop of pressure in any unit length or increment of packing, and that the amount of friction on any increment of contact surface is that proportion of the total friction which is related to the proportion of pressure drop within that increment. Thus for a single set of packing having no dividing walls, the greatest portion of the friction occurs in a small length of the contact, farthest from the source of pressure.

The coefficient of friction is taken to be the relation of the normal applied pressure to the force necessary to move the shaft. Considering a single set of packing with most of the measured friction occurring on a small area, the coefficient for the unit of area will be very high, causing heat and rapid wear within a limited region. The purpose of this invention is not especially to reduce the total measured friction necessary to seal off the pressure, but to distribute the latter quantity so that all of the area in contact does an equal share in creating the friction, which means a uniform distribution of wear and an equal radiation of temperature by a controlled seepage flow.

Referring now to Figure 8, an internal pressure chart, the ordinates being to a scale and being pressures resulting when the constant pressure P is impressed on the packing set of Figure 1, and the abscissas, to a scale now being the actual length of the packing surface in contact with the shaft 2 of Figure 1. The divisional points on the chart, 3, 4, 5, B, and I, represent the confines of the compartments formed by the corresponding cups and retainers 3, 4, 5, 6, and l of Figure 1. The dotted line U is the ideal pressure drop throughout the length of the packing which will qualify any packing structure for the twenty-fourth law of friction, that friction is independent of the area of contact, when the normal applied pressure is equal at all points of the contact.

First, the packing as shown in Figure 1 is considered to be a single set, that is, the division walls are assumed to be removed from Figure 1, the packing rings being adjacent to each other. The packing is therefore subject to a continued seepage flow under the constant impressed pressure, according to the line S of Figure 8, the line S being the actual pressure at any point along the contact surface. It may be observed that the greatest rate of pressure drop is close to the packing gland, at which location most of the friction occurs. To demonstrate the distribution of the friction per increment of length according to the pressure line S, the amounts of friction are plotted as ordinates of the internal-pressure chart, the total friction being assumed to be F, a concrete quantity. The rate of pressure drop is taken for increments of length from the curve S and the proportional value of the total friction F solved for, resulting in the friction curve s, starting at the point 18 as the internal pressure is not reduced up to this point, and ending at point is. The area of contact between the points 28 and I is therefore subjected to most of the strain, resulting in high temperature locally and rapid wear, and giving a high coeiiicient of friction due to the low porosity of the structure, it being compressed by the accumulated thrust. This is the condition of all single sets of fibrous packing.

The condition inherent with the drop of pressure is that there must be seepage flowing thru the packing structure, however minute the necessary amount may be, for when the internal pressure becomes equalized in a packing structure, the effect is the same as replacing the packing gland 1 of Figure 1 with a tight gasket, eliminating the ability of the packing to react against the pressure. An examination of the first and second laws of friction indicates that when some mechanical means is provided to induce a drop of pressure at various intervals along the area of contact that the friction will be distributed over a greater area than is possible with a single set of packing, Referring again to Figure 1, theendwalls of the cups 4, 5 and 6 and the seat in the packing gland I provide the partitions necessary to realize a pressure drop at four points, instead of the one. point of a single set which is the packing gland face. (As yet no consideration is being given to the seepage passages made thru the aforesaid end-walls.)

The use of partitioning walls between packing sections may be termed true multistaging, each compartment being separate and the only communicating passageway being the clearance between the end-walls of the compartments and the shaft. Reference is again made to Figure 8, the effect of multistaging being shown by the internal pressure line M, only the friction arising from the drop of pressure being considered. Applying the first and second laws of friction only, the friction is not found to be distributed between three compartments, appearing in compartment 45, also in 56 and. in 6-l, the value fm being about one-half the value is of a single set. Up to this point, theoretically it is apparent that the maximum friction per unit of area has been reduced by true multistaging and that temperature and wear should be reduced as compared to a single set of packing.

It has been found that for a considerable time after a true multistage packing is put into operation that it produces a great amount of heat accompanied by a severev wearing of the shaft, the effect starting at the inner compartment, passing to the next, and so on thruout the length of contact, failing in service when the last compartment of packing cannot hold the pressure. In Figure 8, the theoretical lines of friction as derived, m, m, m and m do not obtain, but that friction lines 3:1, x2, x3 and x4 are the actual relations of contact, as will now be explained.

As soon as pressure is impressed on the packing set of Figure 1, the packing in the compartment between pieces 3 and 4 is saturated, the volume of occupancy immediately increases, and as the packing rings are in a confined space they are compressed, the porosity is decreased, the seepage flow reduced and the friction of contact increases so that practically all of the pressure is held by the inside compartment. The consequence is that the shaft is worn quickly and the packing rings in the compartment are worn off at their edges of contact, the first compartment of packing starts to leak, whereupon the second compartment becomes saturated and the packing expands, giving the friction line $2. In like manner each succeeding compartment becomes saturated as shown by the lines 333 and an. After the outer and last compartment is worn and begins to leak, the life of the packing and shaft is exhausted as the pressure cannot be held.

Referring again to Figure l, the interposition of the compartment end-walls interferes with the seepage flow that existed in the packing as a single set, the direction and location of the fiow being constricted to the clearances between the end-walls and the shaft. The amount of the flow is also diminished because the porosity of the packing rings as constructed according to Figure 5 is less at the point 'of contact with the shaft and is further restricted by the lowering of the porosity due tothe reaction of the packing against the pressure. It should be apparent that dividing the packing into compartments, thus decreasing the number of paths of the seepage flow as well as the amount of flow, subjects the packing successively in each compartment to the maximum effect of saturation by pressure, bringing about an increase of volume, forcing the rings against the shaft to cause excessive heat and wear until the volume of the packing is reduced to correspond to the saturation condition obtaining. In the meantime the shaft is worn, the packing damaged and the multistage will continue to operate for a time as long as the temperature and pressure remain constant, but will leak badly when idle or while being put into service with varying conditions to contend with.

As the flow of seepage thru a porous elastic structure is the fundamental reason why the packing reacts against and will seal off the impressed pressure, it should be apparent that whatever changes in design are made to distribute the friction of contact, the seepage flow must also be considered as a part of the changes made and must not be restricted in a way to increase the friction. Referring again to Figure 1, the series of seepage passages, l4, l5, I6 and I! provide ample means for the circulation of pressure, thus decreasing the eifect of saturation to the same value as existed in the single set before mentioned. By partitioning the packing into compartments, the desired feature of the distribution of friction is secured, as shown by the internal pressure line MB of Figure 8, the effect of saturation being reflected by the difference between the lines U and MF, it not being practically possible to eliminate all saturation owing to the inequalities of the porosity of any packing structure. The friction lines 172 m and mf appear in each compartment having a maximum value of fmf, Very closely approximating the line of ideal friction at, of a constant value In. To obtain the maximum seepage flow in the compartment adjacent to the impressed pressure, the seepage passages are increased in number and in total area as shown by Figure 4, being decreased in number and total area as the packing is farther from the source of pressure, as respectively shown by Figures 3 and 2.

In designing multistages to meet the various conditions of temperature, the harshness of contact due to packing material in the presence of certain liquids and gases, high speeds and the like, the importance of the amount and of the location of the seepage flow as a means to remove the materials which have been heated, becomes of further importance. While it has been shown that the multistage as constructed according to this invention will obtain a uniform distribution of friction, it should also be apparent that the packing rings could be constructed of such a density and porosity as to prevent the mechanical relations of the multistage from operating. That is, the construction of the packing is equally important in producing a uniform drop of pressure, as are the provisions in the multistage end-walls for transferring the seepage after it has flowed thru the packing structure. The multistage as herein constructed is of little benefit unless the packing structure is made in harmony.

In Figure Q is shown the relations of pressure and friction due to a packing structure having its greatest density at the stufing bcx wall contact and as described in Figure 7. The ordinates to a scale are the impressed pressure R, assumed to be considerably higher than the pressure P of Figure 8. The abscissas to a scale are the actual lengths of the packing contact, the points 3, c, 5, 6 and 1! representing the confines of the compartments formed by the corresponding cups and retainers 3, 4, 5, 6, and l of Figure 1. The packing is first considered to be a single set, there being no end-walls as shown in Figure 1, each packing ring being in contact with another ring. Returning to Figure 9, the internal pressure line S shows a drop of pressure starting at point 3, due to the increased porosity, and the friction line 8 derived from the internal pressure relations by the first and second laws of friction, starts at the point 3, continuing to a maximum value is. The slope of the line s in the area El is less than that of the line 8 of Figure 8, due to the higher rate of seepage flow, indicating that seepage can control the friction to some extent according to the sixth law which is, that for a con stant pressure, friction is inversely proportional to the degree of porosity.

Returning now to Figure 1, the end-walls of the cups and retainers are assumed to be used, the packing being divided into four compartments but without any seepage passages. The internal pressure line M shows an immediate drop in the compartment 3-4 as the increased degree of porosity at the surface of contact permits a considerable flow of seepage. This is refiected in the friction lines m, m, m and m appearing in each compartment with a maximum value of fm, much less than the value is of the single set, and if reduced to the same scale, less than the value fm of Figure 8.

The effect of saturation on the type of packing structure shown in Figure 7 is less than that of Figure 5, as the clearance between the shaft and the end-walls of the compartments is adjacent to that portion of the packing structure having its greatest degree of porosity. Hence this multistage, when so equipped and when first placed in service will not heat so vigorously nor will there be as much wear on the shaft and the packing, as in the case cited under Figure 8. The friction lines yi, yz, ya and 1 4 appearing successively in each compartment indicate less friction and an improvement over the corresponding case of Figure 8, due to increased seepage flow.

Referring again to Figure 1, the series of seepagc passages l4, l5, l6, and i? are considered to be added to the construction, thus establishing multiple paths for any seepage confined in the compartments, the result being the internal pressure line MF, and the corresponding friction lines mf', my, m and mi, closely approximating the uniform friction line 11. of a constant value in.

The multistage constructed according to this invention is solely for constant pressure, or pressure changing at such a rate that there will be at no point of the contact, an excess or an insufficient seepage flow. This multistage however, when designed for different ranges of pressures constant in value must be equipped with packing rings of suitable densities. For the lowest pressure range, the ring structure in Figure 5 gives the lowest friction and best operation. For the next higher pressure range, as well as conditions of increased speed, temperature and higher coefficients of friction due to harsh contacts of liquids and gases, the ring of uniform density as shown in Figure 6 is desirable to increase the fiow of seepage. For extreme cases, the structure of Figure '7 still further increases the seepage flow and counteracts the increasing friction of contact and maintains a higher degree or porosity under reaction. These three general types of ring structure will meet all of the conditions of commercial application. Under operate in like manner to the cone-shape, tho I at a different efficiency.

The object of multistaging a packing is to dis tribute friction over the entire area of contact. It should be apparent that this is automatically accomplished in this design. It should be further apparent that many variations of seepage fiow can be utilized to control the friction between a shaft and a porous structure, made elastic by the impression of pressure, but such variations as are within the scope of the appended claims, I do claim.

What is claimed as new is:

1. A stuffing box assembly made up of packing support rings, packings therein, a gland to position said packing, and a vent through said gland adjacent the outer periphery of the packing so that the fluid leaking through the packing may escape to the atmosphere, said packings being of different densities as arranged in said box so that the friction of contact with the rod will vary along the length of the box.

2. A multistage packing including a plurality of packing stages each adapted to cause a pressure drop, a leak from each stage to the next, and a leak through the gland of the last stage at the outer edge of the packing, said packing rings being of different densities in the different stages.

3. A packing gland for multistage packings including means tapered away from the packed surface to contact the packing, means to hold the gland in position, and means including a passage through the gland at a point spaced from the packed surface for fluid seeping through the packings, and packing rings of different densities arranged therein.

HARLEY T. WHEELER. 

